DE112020001266T5 - High pressure fuel pump - Google Patents

Abstract

An object of the present invention is to stabilize an operation of an intake valve to suppress a decrease in durability or oil-tightness of an intake valve mechanism. Therefore, a high pressure fuel pump 100 of the present invention includes an intake electromagnetic valve mechanism having an intake valve 30, and the intake valve 30 includes: a rod portion 30B; a valve body portion 30A formed integrally with the rod portion 30B; a first guide portion 31B that guides an outer peripheral portion 30B1 of the rod portion 30B; and a second guide portion 34B1 that guides an outer periphery of the valve body portion 30A.

Description

Technical area

The present invention relates to a high pressure fuel pump that includes an intake valve mechanism.

Technical background

As the technical background of the present technical field, there is a high pressure fuel supply pump disclosed in JP 2017-96216 A (PTL 1) is known. The high pressure fuel supply pump according to PTL 1 includes an electromagnetically controlled intake valve mechanism, and paragraphs 0018 to 0021 of PTL 1 describe the following configuration. The electromagnetically controlled inlet valve mechanism contains a piston rod that is electromagnetically controlled. A valve is provided at a distal end of the piston rod and the valve faces a valve seat formed in a valve housing. A piston rod biasing spring is provided at the other end of the piston rod and biases the piston rod in a direction in which the valve is separated from the valve seat (in the valve opening direction). A valve stop is attached to an outer peripheral portion on a remote end face of the valve housing.

The valve stopper is a member that restricts the movement of the valve 203 in the valve opening direction. A valve biasing spring is disposed between the valve and the valve stopper, and the valve is biased in a direction in which it is separated from the valve stopper (the valve closing direction) by the valve biasing spring. Although the valve and the distal end of the piston rod are biased in the opposite directions by the respective springs, the piston rod biasing spring is configured using a stronger spring and thus the piston rod urges the valve against in the direction in which it is separated from the valve seat a force of the valve biasing spring, whereby the valve is pressed against the valve stop.

The piston rod and valve are not attached and a dimension of the distal end of the piston rod is defined such that it can separate from the valve (paragraph 45). The valve stop has a protrusion provided with a cylindrical surface and protruding toward a bottomed cylindrical portion of the valve at its central portion, and the cylindrical surface acts as a guide portion that guides a stroke of the valve in an axial direction ( Paragraph 47).

Citation list

Patent literature

PTL 1: JP 2017-96216 A

Summary of the invention

Technical problem

In the high pressure fuel supply pump of PTL 1, the piston rod of the solenoid operated intake valve mechanism and the valve are not fixed, and the stroke of the valve in the axial direction is guided by the cylindrical surface provided in the projection of the valve stopper. In this case, it is necessary to increase an axial length of the cylindrical surface in order to stabilize operation of the valve in the axial direction, but the increase in the axial length of the cylindrical surface leads to an increase in the size of the intake valve mechanism. In other words, when the axial length of the cylindrical surface is shortened, rectilinear movement of the valve in the axial direction becomes unstable such that the valve abuts the valve seat in a state where the valve is inclined. In this case, wear of the valve (intake valve) or a seat portion of the valve seat (intake valve seat) is great and durability of the intake valve mechanism is lowered, resulting in deterioration of oil tightness at an early stage.

An object of the present invention is to stabilize an operation of an intake valve in order to suppress a decrease in durability or an oil-tightness of an intake valve mechanism.

the solution of the problem

In order to solve the above problems, a high pressure fuel pump of the present invention includes an electromagnetic intake valve mechanism having an intake valve.

• einen Stababschnitt;
• einen Ventilkörperabschnitt, der mit dem Stababschnitt einteilig gebildet ist;
• einen ersten Führungsabschnitt, der einen Außenumfangsabschnitt des Stababschnitts führt; und
• einen zweiten Führungsabschnitt, der einen Außenumfang des Ventilkörperabschnitts führt.

The inlet valve contains the following:

• a rod section;
• a valve body portion formed integrally with the rod portion;
• a first guide portion that guides an outer peripheral portion of the rod portion; and
• a second guide portion that guides an outer periphery of the valve body portion.

Advantageous Effects of the Invention

According to the present invention, it is possible to suppress the decrease in durability or oil tightness of the intake valve mechanism by stabilizing the operation of the intake valve. Other configurations, operations and effects of the present invention will be described in detail in the following embodiments.

Figure list

• [ 1 ] 1 Fig. 13 is an overall configuration diagram of an engine system to which a high pressure fuel pump according to the present invention is applied.
• [ 2 ] 2 Fig. 13 is a cross-sectional view illustrating a vertical cross section (a cross section parallel to an axial direction of a piston) of the high pressure fuel pump which is a premise of application of the present invention.
• [ 3 ] 3 FIG. 13 is a cross-sectional view showing a horizontal cross section (a cross section perpendicular to the axial direction of the piston) of the high pressure fuel pump of FIG 2 illustrated from above.
• [ 4th ] 4th FIG. 13 is a cross-sectional view showing a vertical cross section (a cross section parallel to the axial direction of the piston) of the high pressure fuel pump of FIG 2 from a direction that is different from the in 2 is different, seen illustrated.
• [ 5 ] 5 FIG. 13 is an enlarged cross-sectional view of an electromagnetic intake valve mechanism of FIG 2 .
• [ 6th ] 6th Fig. 13 is a view for describing an operation of an intake valve.
• [ 7th ] 7th Fig. 13 is a view illustrating an example of a variant of configurations of a valve body portion and a guide portion that guides the valve body portion.
• [ 8th ] 8th Fig. 13 is a view illustrating an example of a variant of configurations of a valve body portion and a guide portion that guides the valve body portion.

Description of the embodiments

Embodiments according to the present invention are described below.

1 Fig. 13 is an overall configuration diagram of an engine system to which a high pressure fuel pump is applied 100 according to the present invention is applied. A portion surrounded by a broken line shows a main body of a high pressure fuel pump 100 at (see 2 ) and mechanisms and parts illustrated in this dashed line are incorporated in a pump housing 1 in one piece. Incidentally, is 1 FIG. 13 is a view schematically illustrating an operation of the engine system.

However, although in the following description there is a case where a description is given by setting a vertical direction, the vertical direction uses a vertical direction in FIG 2 and 4th as a basis and does not necessarily coincide with a vertical direction in the case of the high pressure fuel pump 100 is mounted on an engine. In the following description, an axial direction is indicated by a central axis 2A (see 2 ) of a piston 2 and the axial direction is parallel to the central axis 2A of the piston 2 and corresponds to a longitudinal direction of the piston 2.

Fuel in a fuel tank 20 is pumped out by a feed pump 21 based on a signal from an engine control unit 27 (hereinafter referred to as the ECU). This fuel is pressurized to a suitable feed pressure and via an inlet line 28 to a low-pressure fuel inlet opening 10a of the high-pressure fuel pump 100 sent. The low pressure fuel inlet port 10a is configured using an inlet connector 51 (see FIG 3 and 4th ).

The fuel that has passed through the low-pressure fuel intake port 10a reaches an intake port 31b of an intake electromagnetic valve mechanism 300 which constitutes a variable capacity mechanism by means of damper chambers (10b and 10c) in which a pressure pulsation reducing mechanism 9 is arranged.

The fuel that is in the electromagnetic intake valve mechanism 300 flows through the inlet opening (the inlet duct), which is passed through an inlet valve 30th is opened and closed, and flows into a pressure chamber 11. A cam mechanism 93 (see FIG 2 and 4th ) of the prime mover exerts a driving force for an alternating movement on the piston 2. Due to the alternating movement of the piston 2, the fuel is discharged from the inlet opening through the inlet valve 30th is opened and closed, sucked into the pressure chamber 11 in a downward stroke of the piston 2. The fuel that has been drawn into the pressure chamber 11 is pressurized in an upward stroke. The pressurized fuel is through a Dispensing valve mechanism 8 is pumped to a manifold 23 on which a pressure sensor 26 is mounted.

The injector 24 connected to the rail 23 injects the fuel into the engine based on a signal from the ECU 27. The high pressure fuel pump of the present embodiment is a high pressure fuel pump applied to a so-called direct injection engine system, wherein the injector 24 injects fuel directly into a liner of the engine. In the high pressure fuel pump 100 becomes the electromagnetic intake valve mechanism 300 controlled by the signal sent from the ECU 27, and a desired fuel flow rate is discharged through a fuel discharge port 12.

2 Fig. 13 is a cross sectional view showing a vertical cross section (a cross section parallel to the axial direction of the piston 2) of the high pressure fuel pump 100 which is a requirement of application of the present invention. 3 Fig. 13 is a cross-sectional view showing a horizontal cross section (a cross section perpendicular to the axial direction of the piston 2) of the high pressure fuel pump 100 from 2 illustrated from above. 4th Fig. 13 is a cross sectional view showing a vertical cross section (a cross section parallel to the axial direction of the piston 2) of the high pressure fuel pump 100 from 2 from a direction that is different from the in 2 is different, seen illustrated.

A cylinder 6, which guides the reciprocating movement of the piston 2 and, together with the pump housing 1, forms the pressure chamber 11, is attached to the pump housing 1. That is, the piston 2 reciprocates in the cylinder 6 to change the volume of the pressure chamber 11. In addition, the pump housing 1 is provided with the electromagnetic intake valve mechanism 300 configured to supply fuel to the pressure chamber 11 and the discharge valve mechanism 8 configured to discharge the fuel from the pressure chamber 11 to a discharge passage. The cylinder 6 is pressed into the pump housing 1 on its outer peripheral side.

A tappet 92, which converts a rotational movement of the cam 93, which is attached to a camshaft of the internal combustion engine, into an up and down movement and transmits the converted movement to the piston 2, is provided at a lower end of the piston 2. The piston 2 is squeezed toward the plunger 92 by a piston preload spring 4 by means of a holder 15. As a result, the piston 2 can move up and down along with the rotational movement of the cam 93.

An inlet connector 51 is on a side surface of the pump housing 1 of the high pressure fuel pump 100 appropriate. The inlet connector 51 is connected to a low pressure line that carries fuel from the fuel tank 20 to the high pressure fuel pump 100 is supplied, and the fuel is discharged from the inlet connector 51 into the interior of the high pressure fuel pump 100 fed. An inlet filter 52 prevents foreign matter existing between the fuel tank 20 and the low pressure fuel inlet port 10a from flowing into the high pressure fuel pump through the fuel flow 100 be absorbed.

The fuel that has passed through the low-pressure fuel inlet port 10a flows to the pressure pulsation reducing mechanism 9 through a low-pressure fuel inlet passage that extends in the vertical direction in the pump housing 1 arranged.

The fuel that has passed through the damper chambers 10b and 10c then reaches the intake port 31b of the intake electromagnetic valve mechanism via a low-pressure fuel intake passage 10d 300 which extends in the vertical direction in the pump housing 1. Incidentally, the inlet opening 31b is in an inlet valve seat element 31 forming an intake valve seat 31a.

The electromagnetic inlet valve mechanism 300 is provided with a connector 46a. The terminal 46 a is integrally molded with a connector 46 and has an undeformed end connectable to the engine control unit 27.

The electromagnetic inlet valve mechanism 300 is made with reference to 3 exactly described.

In an intake stroke state, the volume of the pressure chamber 11 increases and the fuel pressure in the pressure chamber 11 decreases. In this stroke, when the fuel pressure in the pressure chamber 11 is smaller than the pressure of the intake port 31b, the intake valve becomes 30th switched to the open valve state. When the inlet valve 30th is in a maximum lift state, the intake valve arrives 30th in contact with the stop 32. When the inlet valve 30th is raised, the intake port is between the intake valve seat 31a and the intake valve 30th open and the electromagnetic inlet valve mechanism 300 is open. The fuel passes through the intake port between the intake valve seat 31a and the intake valve 30th and flows into the pressure chamber 11 through a hole (a fuel passage) formed in the pump housing 1 in the transverse direction (the horizontal direction).

After the end of the intake stroke, the piston 2 changes to an upward movement and goes over to the upward stroke. Here, an electromagnetic coil 43 is held in a non-excited state and no magnetic biasing force acts. An anchor preload spring 40 loads an anchor 36 to the right in the drawing (in the valve opening direction) and loads the inlet valve 30th by means of the anchor 36 in the valve opening direction. A preload force of the armature preload spring 40 is adjusted to have a sufficient preload force required to operate the inlet valve 30th in the state in which the electromagnetic coil 43 is not turned on, to be kept open. Although the volume of the pressure chamber 11 decreases along with the upward movement of the piston 2, once the fuel has been taken into the pressure chamber 11, it will return through the inlet port of the inlet valve 30th in the open valve state in this state back to the inlet channel 10d and thus the pressure of the pressure chamber 11 does not increase. This stroke is called a return stroke.

In this state, when a control signal flows from the ECU 27 to the electromagnetic valve mechanism 300 is applied, a current is applied through the terminal 46 through the electromagnetic coil 43 (see 2 ). As a result, a magnetic attraction force acts between a magnetic core 39 and the anchor 36 such that the magnetic core 39 and the anchor 36 be brought into contact with a magnetic surface of attraction. The magnetic attraction force overcomes the biasing force of the armature biasing spring 40 to the armature 36 preload and move the anchor 36 in a direction such that it is from the inlet valve 30th is separated.

At this point, the inlet valve is 30th closed by a biasing force of an intake valve biasing spring 33 and a fluid force generated by the fuel flowing into the intake passage 10d. After the valve is closed, the fuel pressure of the pressure chamber 11 increases along with the upward movement of the piston 2 to be equal to or greater than the pressure of the fuel discharge port 12, the high pressure fuel is discharged through the discharge valve mechanism 8, and the high pressure fuel becomes the rail 23 fed. This stroke is referred to as a delivery stroke.

That is, the upstroke between a lower starting point and an upper starting point of the piston 2 includes the return stroke and the delivery stroke. Then, it is possible to control the amount of high pressure fuel to be discharged by controlling a timing of energization of the coil 43 of the intake electromagnetic valve mechanism 300 to control.

As in 3 As illustrated, the discharge valve mechanism 8 provided at an outlet of the pressure chamber 11 includes a discharge valve seat 8a, a discharge valve 8b that is brought into contact with or separated from the discharge valve seat 8a, a discharge valve spring 8c that connects the discharge valve 8b to the discharge valve seat 8a, and a discharge valve stop 8d that defines a stroke (a moving distance) of the discharge valve 8b. The discharge valve stop 8d and the pump housing 1 are connected to one another by welding at an abutment section 8e in order to shut off a flow path through which fuel flows from the outside.

In a state where there is no fuel pressure difference between the pressure chamber 11 and a discharge valve chamber 12a, the discharge valve 8b is pressed against the discharge valve seat 8a by a biasing force generated by the discharge valve spring 8c and is switched to a valve closed state. The discharge valve 8b is open against the discharge valve spring 8c when the fuel pressure in the pressure chamber 11 becomes greater than the fuel pressure in the discharge valve chamber 12a. The fuel discharge port 12 is formed in a discharge connector 60, and the discharge connector 60 is welded and fixed to the pump housing 1 at a welding portion 60a.

Then, referring to FIG 2 described.

The restriction valve mechanism 200 includes a restriction body 201, a restriction valve 202, a restriction valve holder 203, a restriction spring 204 and a spring stopper 205. The restriction valve 202 is loaded with a load of the restriction spring 204 by means of the restriction valve holder 203 which is pressed by a seat portion of the restriction body 201 and cooperates with the seat section to shut off the fuel.

When the pressure of the fuel discharge port 12 is due to a failure of the intake electromagnetic valve mechanism 300 the high pressure fuel pump 100 is abnormally high and exceeds a target pressure of the limit valve mechanism 200, the abnormally high pressure fuel is discharged to the damper chamber 10c on the low pressure side through a restriction passage 213. However, although the damper chamber 10c is a restriction target of the restriction valve mechanism 200 in the present embodiment, it may the pressure chamber 11 can be set as the limitation target.

The electromagnetic inlet valve mechanism 300 is made with reference to 5 described in more detail. 5 Fig. 13 is an enlarged cross-sectional view of the intake electromagnetic valve mechanism 300 from 2 .

The inlet valve 30th includes a valve body portion 30A , a rod section 30B and a guided portion (a convex portion) 30C. In the present embodiment, the guided section becomes 30C as part of the valve body portion 30A considered and is the guided section 30C in the valve body section 30A educated. An outer diameter f30A of the valve body portion 30A is larger than an outer diameter of the rod portion 30B , the valve body portion 30A forms a larger diameter section with respect to the rod section 30B and the rod section 30B forms a smaller diameter portion with respect to the valve body portion 30A .

The rod section 30B has a rod shape (a round rod shape or a column shape) that has a circular cross section. The valve body portion 30A has a disk shape or a column shape, with a thickness dimension D30A of the rod portion 30B in the axial direction (the longitudinal direction) is smaller with respect to the outer diameter f30A. The rod section 30B is with the valve body portion 30A configured in one piece such that its axial direction is perpendicular to an end face 30A1 of the valve body portion 30A is. The rod section 30B and the valve body portion 30A can be elements that have been formed in one piece, or can be formed by joining one element that forms the rod section 30B and a member that forms the valve body portion 30A forms are obtained.

The end face 30A1 of the valve body portion 30A forms a seat portion, which is the seat portion 31a, in the intake valve seat element 31 is formed facing and is used for a fuel seal portion. For this reason, the seat portion 30A1 has the valve body portion 30A a surface that is processed with a high surface accuracy (ie a low surface roughness).

An outer cylindrical surface (an outer peripheral surface) 30B1 of the rod portion 30B forms a guided portion (a first guided portion) through which movement of the rod portion 30B in the axial direction (the longitudinal direction) by a guide portion (a first guide portion) 31B formed in the intake valve seat member 31 is formed, is performed. Incidentally, is the guide section 31B as an inner cylindrical surface (an inner circumferential surface) included in the intake valve seat member 31 is formed, configured. The outer peripheral surface 30B1 of the rod section 30B and the inner peripheral surface 31B of the inlet valve seat element 31 have surfaces that are processed with a high level of surface accuracy (ie a low surface roughness). As a result, if the rod section 30B on the guide section 31B is prevented from sliding on an inner cylindrical portion of the guide portion 31B is fixed or is closed.

The convex section 30C is on a surface (an end face) 30A2 of the valve body portion 30A formed on a side opposite to the seat portion 30A1. A valve stop 34 is on the end face 30A2 and the convex portion side 30C of the valve body portion 30A intended. The valve stop 34 surrounds the valve body portion 30A through a side wall (a peripheral wall) 34A2 of a concave large diameter portion 34A, thereby forming a valve body housing that contains the valve body portion 30A records. The valve stop also has 34 from the intake valve poppet side 31 seen a stepped concave portion with at least two steps around the valve body portion 30A and the convex section 30C to record.

A bottom surface (a bottom surface of an opening-side concave portion) 34A1 of the large-diameter concave portion (the opening-side concave portion) 34A of the valve stopper 34 lies on the end face 30A2 of the valve body portion 30A thereby forming a stopper portion (a stopper surface) that controls the movement of the valve body portion 30A restricted in the valve opening direction. A bottom surface (a bottom surface of a deep side concave portion) 34B2 of a small diameter concave portion (a deep side concave portion) 34B of the valve stopper 34 forms a spring seat of the intake valve preload spring 33.

The intake valve bias spring 33 is between the bottom surface 34B2 of the small-diameter concave portion and an end surface 30C1 of the convex portion 30C arranged and loads the entire inlet valve 30th in the valve closing direction by means of the valve body portion 30A before. The inlet valve bias spring 33 is flush with the bottom surface 34B2 of the valve stop 34 in direct contact. The bottom surface 34B2 of the valve stop 34 is perpendicular to a central axis LA of the guide section 31B that is in the intake valve seat element 31 is formed and prevents the Inlet valve preload spring 33 is attached in an inclined manner.

The valve stop 34 has one or more openings (cutouts) 34D configured to define a fuel flow path. The opening (cutout) 34D that is configured is the fuel flow path provided in the valve stop 34 is intended to be formed may have a hole shape or a groove shape.

An inner diameter of the small diameter concave portion 34B of the valve stopper 34 is slightly larger than an outer diameter f30C of the convex portion 30C and an outer peripheral surface (a guided portion) 30C2 of the convex portion 30C slides on an inner cylindrical portion (an inner peripheral surface) 34B1 of the small-diameter concave portion 34B. That is, the outer peripheral surface 30C2 of the convex portion 30C forms a guided portion (a second guided portion) and the inner peripheral surface 34B1 forms a guide portion (a guide surface) that guides the guided portion 30C2. This way it is in the inlet valve 30th the guided portion 30C2 of the convex portion 30C provided at one end through the guide portion (the second guide portion) 34B1 of the valve stopper 34 guided to move in the axial direction.

The rod section 30B and the convex section 30C in the inlet valve 30th are at both ends by the guide section 31B that is in the intake valve seat element 31 is formed, or the guide section 34B1 , the one in the valve stop 34 is formed, supported, and movement in the radial direction and a range of inclination are restricted. Each of the guide section 31B that is in the intake valve seat element 31 is formed, and the guide portion 34B1 , the one in the valve stop 34 is formed with a spacing with respect to each of the guided section 30B1 of the rod section 30B and the guided portion 30C2 of the convex portion 30C provided and the inlet valve 30th can with respect to the guide section 31B and the guide section 34B1 slide in an environment where the sliding resistance is small.

The inlet valve seat element 31 is with a fuel seal portion 31a perpendicular to the central axis LA of the guide portion 31B provided and has a surface that is processed with a low surface accuracy.

The valve stop 34 will be described again. The valve stop 34 includes stop surface 34A1 and a surface 34E that engages with the intake valve poppet 31 comes into contact, and the valve body portion 30A showing the convex section 30C is accommodated between these surfaces 34A1 and 34E, and a distance between the stopper surface 34A1 and the surface 34E is defined as ΔL. When t30A is a thickness of the valve body portion only 30A without the convex portion 30C is, a value g1 (see 6th ) of ΔL - t30A as a stroke length of the intake valve 30th be adjusted. A tapered portion 34A3 is on the valve stop side 34 of the inlet valve 30th provided and a contact surface between the valve stop 34 and the valve body portion 30A is decreased to prevent the inlet valve 30th at the valve stop 34 adheres. In addition, a fuel passage area is increased by providing the taper portion 34A3. In addition, the fluid resistance is decreased during valve opening to stabilize the valve opening behavior by providing the tapered portion 34A3.

The inlet valve seat element 31 is in an inner cylindrical section 1H2 (see 3 ), which is provided in the pump housing 1, pressed in or inserted. The valve stop 34 is pressed or inserted into an inner cylindrical portion 1H1 provided in the pump housing 1. The inner cylindrical portions 1H1 and 1H2 provided in the pump housing 1 are formed coaxially and the coaxial accuracy of the intake valve 30th with the guide section 31B and the guide section 34B1 can be increased as the coaxial accuracy is improved.

As an axial length of the guide portion 31B of the inlet valve seat element 31 is small, there may be a sliding surface with respect to the intake valve 30th so held down that it is small. As an axial length of the guide portion 34B1 of the valve stop 34 is small, the sliding surface can be with respect to the inlet valve 30th so held down that it is small. In addition, since the convex portion 30C is formed in a spherical shape, the intake valve 30th in accordance with a relative positional deviation between the intake valve 30th and the seat portion 31a may be inclined after component assembly when the intake valve 30th and the seat section 31a are closed in such a way that it is possible to prevent wear caused by partial stop of the intake valve 30th or an increase in a contact surface pressure between a corner of the guide portion 31B of the inlet valve seat element 31 and the rod section 30B is caused to hold down.

6th Fig. 13 is a view for describing an operation of the intake valve 30th . 6 (A) Fig. 11 illustrates a state when the valve is open. 6 (B) illustrates a state during a transition from an open state to a closed state. 6 (C) Fig. 11 illustrates a state when the valve is closed.

In the state of 6 (A) g1 is a gap G1 between the seat portion 30A1 of the valve body portion 30A and the seat portion 31a, and g2 is a gap G3 between an end face 36A of the armature 36 and an end face 39A of the magnetic core 39 . In this case, g2 is greater than g1 (g2> g1). Incidentally, there are an end section 30B2 of the rod section and an end face 36B of the anchor 36 to each other and is a gap G2 between the end portion 30B2 and the end surface 36B 0 (G2 = 0).

In the state of 6 (B) is the gap G1 between the seat portion 30A1 of the valve body portion 30A and the seat portion 31a 0 (G1 = 0) and is the gap G3 between the end face 36A of the armature 36 and the end face 39A of the magnetic core 39 g3. In this case, g3 is a quantity obtained by subtracting g1 from g2 (g3 = g2 - g1). Incidentally, there are an end section 30B2 of the rod section and an end face 36B of the anchor 36 to each other and is a gap G2 between the end portion 30B2 and the end surface 36B 0 (G2 = 0).

In the state of 6 (C) is the gap G1 between the seat portion 30A1 of the valve body portion 30A and the seat portion 31a 0 (G1 = 0) and is the gap G3 between the end face 36A of the armature 36 and the end face 39A of the magnetic core 39 also 0 (G3 = 0). In this case, the end portion 30B2 of the rod portion and the end face 36B of the anchor 36 separated in a direction along the central axis LA, a gap becomes between the end portion 30B2 of the rod portion and the end face 36B of the anchor 36 and is the gap G2 between the end portion 30B2 and the end face 36B g3.

Variants of the configurations of the valve body 30A and the guide portion that the valve body 30A leads are described. 7th and 8th are views showing examples of variations of the configurations of the valve body 30A and the guide portion that the valve body 30A leads, illustrate.

In 7th the convex portion 31C is not provided, and the outer peripheral portion (the outer peripheral surface having the largest outer diameter) of the valve body portion serves 30A than the guided section 30C2. In this case, 30C2 is not the outer peripheral surface of the convex portion 31C.

In this example both are the first guide section 31B as well as the second guide section 34B1 using the inlet valve poppet 31 configured. For example, a portion of the side wall (peripheral wall) 34A2 of the valve stop 34 using the inlet valve poppet 31 configured. Even in this case, the first guided portion 31B1 is in the rod portion 31B and the second guided portion 30C2 is in the valve body portion 30A educated. It should be noted that in the present example, the coaxiality of the first guide section 31B and the second guide section 34B1 is held. As long as the coaxiality of the first guide section 31B and the second guide section 34B1 is held, it is unnecessary to use the first guide section 31B in the inlet valve seat element 31 provide, and a further element, the first guide section 31B forms, can be provided.

In 8th is the first guide section 31B that is in the intake valve seat element 31 in 7th is formed as in the embodiment of FIG 5 in the valve stop (the valve housing) 34 is provided. In this case, the second guided portion 30C2 is configured the same as that of FIG 7th .

In the examples referring to 7th or 8th are described, the second guide portion 34B1 that is in the intake valve seat element 31 or the valve stop (the valve housing) 34 is provided, be formed in the pump housing 1. In this case it is because there is some form of valve stop 34 is formed directly on the pump housing 1, another component for the valve stop is unnecessary 34 to be assembled with the pump housing 1. As a result, it is possible to improve assembly work efficiency and reduce material cost.

1. (1) Der elektromagnetische Einlassventilmechanismus 300, der das Einlassventil 30 besitzt, wird geschaffen und das Einlassventil 30 enthält Folgendes: den Stababschnitt 30B; den Ventilkörperabschnitt 30A, der mit dem Stababschnitt 30B einteilig gebildet ist; den ersten Führungsabschnitt 31B, der den Außenumfangsabschnitt 30B1 des Stababschnitts 30B führt; und den zweiten Führungsabschnitt 34B1, der den Außenumfang des Ventilkörperabschnitts 30A führt.
2. (2) In (1) führt der zweite Führungsabschnitt 34B1 den Außenumfang des konvexen Abschnitts 30C, der auf einer abgelegenen Stirnseite des Ventilkörperabschnitts 30A gebildet ist.
3. (3) In (1) sind der erste Führungsabschnitt 31B und der zweite Führungsabschnitt 34B1 koaxial konfiguriert.
4. (4) In (3) ist das Einlassventilsitzelement 31, auf das der Ventilkörperabschnitt 30A aufgesetzt ist, vorgesehen und ist der erste Führungsabschnitt 31B unter Verwendung des Einlassventilsitzelements 31 konfiguriert.
5. (5) In (4) ist ein Ventilkörpergehäuseabschnitt 34, der als ein vom Einlassventilsitzelement 31 getrenntes Element gebildet ist, vorgesehen und ist der zweite Führungsabschnitt 34B1 unter Verwendung des Ventilkörpergehäuseabschnitts 34 konfiguriert.
6. (6) In (2) ist der Außendurchmesser f30C des konvexen Abschnitts 30C kleiner als der Außendurchmesser f30A des Ventilkörperabschnitts 30A.
7. (7) In (3) ist der zweite Führungsabschnitt 34B1 im Pumpengehäuse 1 gebildet, an dem der elektromagnetische Einlassventilmechanismus 300 angebracht ist.
8. (8) In (1) enthält der elektromagnetische Einlassventilmechanismus 300 den Anker 36 und den Magnetkern 39, die die magnetischen Anziehungskräfte wechselseitig erzeugen, liegen der Anker 36 und der Stababschnitt 30B während des Ventilöffnens aneinander an, werden der Anker 39 und der Stababschnitt 30B während des Ventilschließens voneinander getrennt und wird während des Ventilöffnens die Lücke g3 zwischen den Widerlagerabschnitten 36B und 30B2 des Ankers 36 und des Stababschnitts 30B erzeugt.
9. (9) Der elektromagnetische Einlassventilmechanismus 300, der den Anker 36, den Magnetkern 39, das Einlassventil 30 und das Einlassventilsitzelement 31 enthält, wird geschaffen. Das Einlassventil 30 ist derart befestigt, dass der Ventilkörperabschnitt 30A, der am Einlassventilsitzelement 31 anliegt, um eine Abdichtung gegen Kraftstoff zu schaffen, und der Stababschnitt 30B, der vom Ventilkörperabschnitt 30A zum Anker 36 verläuft, immer einteilig arbeiten, und enthält den ersten Führungsabschnitt 31B, der den Außenumfangsabschnitt 30B1 des Stababschnitts 30B führt, und den zweiten Führungsabschnitt 34B1, der den Außenumfang des Ventilkörperabschnitts 30A führt.

Features of the high pressure fuel pump 100 according to the present embodiment, for. B. listed as follows.

1. (1) The electromagnetic intake valve mechanism 300 holding the inlet valve 30th owns, is created and the inlet valve 30th contains: the rod section 30B ; the valve body portion 30A , the one with the rod section 30B is formed in one piece; the first guide section 31B , which is the outer peripheral portion 30B1 of the rod section 30B leads; and the second guide section 34B1 , which is the outer periphery of the valve body portion 30A leads.
2. (2) The second guide section leads in (1) 34B1 the outer circumference of the convex portion 30C that is on a remote end face of the valve body portion 30A is formed.
3. (3) In (1) are the first guide section 31B and the second guide section 34B1 configured coaxially.
4. (4) In (3) is the intake valve seat member 31 on which the valve body portion 30A is placed, provided and is the first guide section 31B using the inlet valve poppet 31 configured.
5. (5) In (4) is a valve body housing portion 34 serving as one of the intake valve seat member 31 separate member is formed, is provided and is the second guide portion 34B1 using the valve body housing section 34 configured.
6. (6) In (2), the outer diameter is f30C of the convex portion 30C smaller than the outer diameter f30A of the valve body portion 30A .
7. (7) In (3) is the second guide section 34B1 formed in the pump housing 1 on which the electromagnetic inlet valve mechanism 300 is appropriate.
8. (8) In (1) includes the intake valve electromagnetic mechanism 300 the anchor 36 and the magnetic core 39 that mutually generate the magnetic forces of attraction, lie the armature 36 and the rod section 30B while the valve is opening, become the armature 39 and the rod section 30B separated from each other during valve closing and the gap g3 between the abutment portions 36B and 30B2 of the armature becomes during valve opening 36 and the rod section 30B generated.
9. (9) The electromagnetic intake valve mechanism 300 holding the anchor 36 , the magnetic core 39 , the inlet valve 30th and the intake valve seat member 31 contains is created. The inlet valve 30th is attached such that the valve body portion 30A , the one on the inlet valve seat element 31 rests to create a seal against fuel, and the rod portion 30B from the valve body portion 30A to the anchor 36 runs, always work in one piece, and contains the first guide section 31B , which is the outer peripheral portion 30B1 of the rod section 30B leads, and the second guide section 34B1 , which is the outer periphery of the valve body portion 30A leads.

In the embodiment according to the present invention, the valve body portion 30A and the rod section 30B an integrated structure and become both end portions of the seat portion 30A1 of the intake valve 30th carried so that the inclination of the inlet valve 30th when the inlet valve 30th opened and closed can be restricted to be small. As a result, the possibility that the inlet valve 30th or the corner of the intake valve seat 30A1 in contact with the seat portion 31a of the intake valve seat member 31 , damages the seat portion 31a and deteriorates the oil tightness, can be held down to be low.

According to the present invention, it is possible to reduce the deterioration in oil tightness by reducing the inclination of the intake valve 30th in the electromagnetic intake valve mechanism 300 hold down so that it is possible to use the high pressure fuel pump 100 that realizes a cost reduction by reducing the number of components.

List of reference symbols

30th

Inlet valve

30A

Valve body section

30B

Rod section

30B1

Outer peripheral portion of the rod portion 30B

30C

Convex section

31

Inlet valve seat element

31B

First section of the tour

34

Valve stop (valve body housing section)

34B1

Second guide section

36

anchor

39

Magnetic core

100

High pressure fuel pump

300

Electromagnetic inlet valve mechanism

QUOTES INCLUDED IN THE DESCRIPTION

This list of the documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent literature cited

• JP 2017096216 A [0002, 0005]

Claims (9)

A high pressure fuel pump comprising an electromagnetic inlet valve mechanism having an inlet valve, the inlet valve including: a rod section; a valve body portion formed integrally with the rod portion; a first guide portion that guides an outer peripheral portion of the rod portion; and a second guide portion that guides an outer periphery of the valve body portion. High pressure fuel pump after Claim 1 wherein the second guide portion guides an outer periphery of a convex portion formed on a distal end face of the valve body portion. High pressure fuel pump after Claim 1 wherein the first guide portion and the second guide portion are configured coaxially. High pressure fuel pump after Claim 3 Further comprising: an intake valve seat member on which the valve body portion is fitted, wherein the first guide portion is configured using the intake valve seat member. High pressure fuel pump after Claim 4 Further comprising: a valve body housing portion formed as a separate member from the intake valve seat member, the second guide portion configured using the valve body housing portion. High pressure fuel pump after Claim 2 configured such that an outer diameter of the convex portion is smaller than an outer diameter of the valve body portion. High pressure fuel pump after Claim 3 wherein the second guide portion is formed in a pump housing to which the electromagnetic intake valve mechanism is attached. High pressure fuel pump after Claim 1 wherein the electromagnetic intake valve mechanism includes an armature and a magnetic core that mutually generate magnetic attraction forces, and the armature and the rod portion abut against each other during valve opening, the armature and the rod portion are separated from each other during valve closing, and a gap between the armature and the rod portion is produced. High pressure fuel pump, which includes: an electromagnetic intake valve mechanism including an armature, a magnetic core, an intake valve, and an intake valve seat member, wherein the inlet valve is attached in such a way that a valve body portion, which rests against the inlet valve seat element in order to seal against fuel, and a rod portion, which extends from the valve body portion to the armature, always work in one piece, and Includes: a first guide portion that guides an outer peripheral portion of the rod portion; and a second guide portion that guides an outer periphery of the valve body portion.

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